Grinding machinery



Oct. 9, 1934. F. s. HAAS GRINDING MACHINERY.

Filed Aug. 27, 1950 3 Sheets-Sheet 2 F. S. HAAS GRINDING MACHINERY Oct. 9, 1934.

A Filed Aug. 27, 1930 E; yig

3 Sheets-Sheet 3 Patented Oct. 9, 1934 UNITED STATES PATENT OFFICE GRINDING MACHINERY Application August 27, 1930, Serial N o. 478,127

7 Claims.

This invention relates to improvements in machine tools Aand especially to improvements in control mechanism for controlling the move-- ment of movable members remote from the operator and generally in inaccessible positions.

One of the principal objects of the invention, therefore, is the provision of an improved novel control mechanism for use with machinevtools or the like for initiating and controlling the 10 movements of units or parts thereof.

Another object of the invention is the provision of improved means for selectively effecting and controlling the movements of units or parts of a machine tool organization which are remote from one another and from the operator.

A further object of the invention is the provision of a novel improved mechanism for actuating the control valves of an hydraulic pressure circuit for selectively controlling the movements of Widely spaced unitsA or parts of a machine tool organization which are adapted to be selectively actuated by hydraulic pressure.

A still further and specific object of the invention is the provision of improved hydraulic means fo'r controlling the redressing or retrueing tools of a centerless grinder, together with a single improved means for selectively operating either the grinding wheel orthe regulating wheel trueing mechanism and for simultaneously effecting the infeed and traverse feed of the `selected trueing mechanism. I

Other objects and advantages of the present invention should be readily apparent by reference to the following specication considered in commotion with the accompanying drawings forming a part thereof, and it is to be understood that any modifications may bemade in the exact structural details there shown Without departing from or exceeding the spirit of the invention as I defined by the appended claims.

Figure 6 is a sectional view on line 6 6 of Figure 4.

Figure 7 is a sectional View on line 7 7 of Figure 2.

Figure 8 is a sectional view on line 8 8 of Figure 2.

Figure 9 is a fragmentary sectional view on 60 line 9 9 of Figure '7.

Figure 10 is a diagrammatic view of the hydraulic circuit employed with this invention.

Throughout the several views of the drawings similar reference characters are employed to denote the same or similar parts.

In the drawings a centerless grinder hasv been employed to illustrate the invention, but it' is to be understood that any other type of grinding machine may have the improved trueing mechanism here illustrated and described applied thereto. It is to be further understood that while the invention is illustrated as controlling a plurality of trueing mechanisms, it is equally applicable for controlling a single such mechanism, as well as controlling other moveable members or units of a machine tool organization. The machine illustrated in Figure 1 comprises a bed or support 15 having securely mounted on one end thereof, for rotation at a high or grinding rate of speed, a grinding wheel spindle and its grinding wheel 16. Opposed to the grinding wheel 16 is a regulating wheel 17 rotatable at a relatively slow work controlling rate of speed. This regulating Wheel is supported by a unit 18 85 having a slide 19 actuable relative to a second slide 20 toward and from the grinding Wheel 16. The said lower slide 20 is in turn supported by the bed 15 for movement with the unit 18 and slide 19 through suitable clamps 21. An adjust- 90 ing screw 22 rotatably, but not translatably, supported by a bracket 23 carried by the bed 15, is employed for effecting said adjustment of the regulating Wheel unit 18 toward and from the grinding wheel 16 through the intermediary of 95 a lever or handle 24.

The operative faces of the Wheels 16 and 17 are spaced from one another to provide a grinding throat in which the work to be operated upon by the said wheels is mounted. This work 25 is peripherally supported by a Work rest blade 26 carried by a block 27, in turn supported by the inner end of the lower slide 20.

The said active faces of the wheels 16 and 17 must be maintained at a high degree of sharpness and trueness to produce work of the desired finish and size. The said wheels are maintained in such condition by trueing tools here shown as diamonds 28 and 29, the former for operation on the grinding wheel andthe latter for similar operation on the regulating wheel. The mechanisms for effecting the movements of the said diamonds being substantially duplicates of one another, it is deemed suliicient if but one of them be described in detail. Accordingly, the diamond or trueing tool 28 is carried by an axially adjustable barrel 30 having a bore 31 in one end thereof, receiving a nut 32, and provid- Ving clearance for an adjusting screw 33 threadedly received by the said nut 32. The barrel 30 is provided with a spline 34 receiving a pin or key 35, so that the movement of the said barrel is truly axial and rotative movement prohibited. The key or pin 35 extends through a guide sleeve 36 encasing the barrel 30. The sleeve 36 has formed at its upper end a counter-bore 37 in which is mounted bearing 38 forming a journal for the reduced portion 33A of the adjusting screw 33. The bearing 38 is further formed with a sleeve portion 39 on which is rotatably mounted a segmental gear 40. The segmental gear 40 has pivotly secured thereto a pawl 41 cooperating with a ratchet 42 keyed or otherwise secured to the said reduced portion 33A of the adjusting screw. A spring 43 maintains engagement between the pawl 41 and ratchet 42. As seen in Figure 6, Athe guide sleeve or housing 36 is formed'at its upper end with a cylinder 44 in which a reciprocable piston or motor 45 is mounted, having formed at one side thereof rack teeth 46 meshing with the teeth of the segmental gear 40. The said piston 45 is adapted to be actuated by hydraulic fluid under pressure. An adjustable stop 47 is carried by one head of the cylinder 44 to limit the movement of the piston 45.

From the foregoing it will be noted that as the piston 45 is shifted from one end of the cylinder to the other, the segmental gear 40 will be actuated rst in one direction and then in the other direction. This oscillation or rocking of the gear 40 first causes the pawl 41 to ride over the teeth of the ratchet 42, whereupon a reverse movement of the piston 45 will, through the inter-engagement of the pawl 41 and ratchet 42, cause a rotation of the ratchet in the said direction. This rotation or movement of the ratchet 42 rotates the adjusting screw 33, thereby feeding the trueing tool barrel 30 axially toward the grinding wheel. From this it will be seen that the piston 45 constantly feeds the barrel 30 in one direction. To retract the diamond, as when replacing either the grinding or regulating wheel, resort may be had to a hand wheel 48 fixed to the outer end of the adjusting screw 43. In practice, the piston is normally in the position opposite to that shown in Figure 6, at which time throw-out 49 engages the outer end of the pawl 41 and holds the same out of engagement with the ratchet 42, so that the adjusting screw 33 may be actuated in either direction through the hand wheel 48, thereby retracting the diamond or trueing tool 28 from the face of the grinding wheel. l

The said diamond or trueing tool 28 is adapted to be actuated transversely of the grinding Wheel by the hydraulic medium under pressure. For this purpose the guide sleeve or casing 36 is provided with a slide 50 having formed therein a dove-tailed guideway 51 receiving a complementary shaped'guide tongue 52, extending from slide 53. The said slide 53 is secured to and supported by a base 54 in turn mounted on a ledge or shelf 55 extending from the guards or housings 56 and 57, respectively surrounding the grinding and regulating wheels 16 and 17. As shown in Figure 5, the slide 55 has secured to one end thereof a bracket 58 forming one head for a cylinder 59, closed at its opposite end by head 60. The bracket or cylinder head 58 also forms a guide 61 for piston rod 62 extending from a piston 63 received in the cylinder 59 and adapted to be actuated longitudinally therethrough. The cylinder head 60 supports an adjustable stop 64 limiting the movement of the cylinder 63 in one direction.

From the foregoing it will be seen that the trueing tool or diamond is actuated transversely of the face of the-abrasive wheels by hydraulic` pressure to remove or true up the said surfaces, an amount determined by the infeed of the said diamond under the inuence of the piston 45. Said pistons 45 and 63 are controlled by a single element, as disclosed in Figures 2, 3, 7, 8 and 9.

The above noted control mechanism is mounted in a housing or casing 65, here shown as depending from the lower surface of the shelf 55 of the grinding wheel housing 56. Mounted within the said casing or housing 65 is a valve lock 66 having a pair of vertical bores 67 and 68 formed therein, each receiving a valve sleeve 69 and 70. A sliding valve 71 and 72 are respectively mounted within the sleeves 69 and 70, the former controlling the actuation of the regulating wheel trueing mechanism and the latter controlling the grinding wheel trueing mechanism. Each valve has depending from it a stem '73 ad 74 respectively supporting a spool 75 and '76. The spools are loosely mounted about their stems and each abuts on its upper end a spring 77 and 78, which in turn respectively abut the lower end of sliding valves 7l and rI2. A similar spring '79 and 80 surrounds the valve stems '73 and 74 abutting respectively with the lower ends of the spools 75 and 76, and with a head 81 and 82 formed on the endsv of the stems 13 and 74. A valve actuator 83 having. a knob 84 on its outer end and an enlarged head 85 on its inner end is provided, being universally mounted as by ball support 86 formed intermediate its ends for movement in several directions, as will be explained. The ball 86 is mounted in a socket 87 carried by a boss 88 formed on the housing or casing 65. A guide plate 89 is mounted interiorly of the casing or housing 65, and has extending therethrough the actuator 83. The guide plate 89 is provided with a central rib 90 defining the path of movement of the actuator 83 through two distinct vertical channels 91 and 92. A third or horizontal channel 93 is provided beneath the central rib communicating with the channels 91 and 92.

The enlarged head portion 85 of the actuator 83 is adapted to be received in the annular groove formed in each of the spools 75 and 76, as shown in Figure 2. The operation of the actuator 83 is as follows. Through the knob 84 the said actuator is moved to bring the same in alignment with channel 93, whereupon it is moved either to the right or the left into either channel 91 or 92 depending upon whether the grinding or regulating wheel is to be trued, the

channel 91 being utilized for the regulating y right, as seen in Figure 5, and a movement of piston 4 5 to the left, as seen in Figure 6, while l actuate the piston 63 at a fast or rapid traverse rate, the actuator 83 would be depressed or raised to the limit of its movement for by-passing the discharge medium, as will be later made clear. As shown in Figure 2, the by-pass line 94 kis controlled by a spring shut-off valve 95, having a plunger 96 extending therefrom. The plunger 96 contacts with a tongue or actuator 97 pivotally mounted at 98 to the casing or housing 65. An adjustable abutment 99 extends from the actuator 97 for engagement with a pair of sliding pins 100, shown most clearly in Figure 7.

vThe sliding pins 100 are supported by a bracket member 101 depending interiorly of the casing or housing 65. The inner ends of the sliding pins 100 are in alignment With the bevel faces 102 and 103 formed on each of the spools 75 and 76. From this it will be seen that as the actuator 83 is shifted to the limit of its movement in a vertical direction, either of the faces 102 and 103 will axially shift the pins 100 for rocking the actuator 97 about its pivot 98 and depressing spring closed plunger 96 through the tongue or actuator 97, thereby opening said valve and bypassing the hydraulic medium through an unrestricted conduit.

The complete operation of the circuit is most clearly illustrated in the diagrammatic hydraulic circuit diagram shown in Figure 10, to which reference is now to be had. A tank or sump 104 is provided for the hydraulic medium which is drawn therefrom through suction pipe 105 by pump 106 and discharged from the said pump through conduit 107. The conduit 107 conveys the medium to the valve block 66 and discharges same into port 108. The port 108 has three branch ports 109, 110, and 111. Each of these ports communicates with valve bores 67 and 68 for delivering the hydraulic medium under pressure to the valves 71 and 72 for distribution thereby. As shown in Figure 10, the medium under pressure is being utilized for actuating the trueing mechanism of the regulating wheel, While the mechanism for trueing the grinding wheel is held stationary. Accordingly the valve 72 is in a neutral position, while the valve 71 is depressed to its operative position for actuating the pistons 45 and 63 at their normal feeding rates. As shown in this figure the hydraulic medium under pressure passes from port 110 into the passage provided by cannelure 112 to ports 113 and 114. The said ports are respectively connected by conduits 115 and 116 with the outer ends of cylinders 44 and 59 for actuating pistons 45 and 63 respectively, the former feeding the diamond or trueing tool toward the regulating Wheel and the latter effecting a traverse movement of the said diamond or trueing tool across the face of the said regulating Wheel. The hydraulic medium Within the cylinders 44 and 59 ahead of the pistons 45 and 63 is discharged respectively through conduits 117 and 118 for delivery to valve ports 119 and 120. The medium from conduit 117 is connected by cannelure 121 with the discharge port 122 and conduit 123 for return to the tank or sump 104, While the medium in conduit 118 is Iconnected Aby cannelure 124 with port 125, conduit 123A and conduit 123 for discharge to the tank or sumpA 104. The hydraulic medium under pressure in the ports 109 and 111 are respectively blocked by the spool portions of the valves 71 and 72, as will be evident from a study of Figure 10.

To return the parts to ltheir normal position the valve actuator 83 is raised for lconnecting the pressure ports 109 and 111 with the former exhaust conduits 117 and 118, and connecting the former pressure conduits 115 and 116 with the discharge ports 122 and 125 and discharge conduit 123. The circuit would then be, considering the valve 71 elevated as respects Figure 10 for connecting port 109 with port 117 through the cannelure 121 and port 111 with the port 120 through the cannelure 126. At this time the hydraulic medium under pressure will simultaneously ow through conduits 117 and 118 discharging the medium Within the cylinders through conduits 115 and 116 to ports 113 and 114 for connection respectively with port 122 through cannelure 112 and port 125 through cannelure 124.

The actuation of the grinding Wheel trueing mechanism is identical, except that the actuator 83 would be moved through the channel 93 to channel 92 for engagement with the spool 76 to actuate the valve 72. It is believed that a specic description of the circuit for effecting and controlling the grinding wheel trueing pistons is unnecessary, but the corresponding ports and conduits have been indicated by the same numbers as used for controlling the regulating Wheel trueing pistons with the addition of a prime thereto.

By reference to Figure 10 it will be seen that discharge line 123A is provided with an adjustable throttle or needle valve 130 before it connects with the common discharge line 123 and that this throttle valve is by-passed by the spring controlled valve 95 while the discharge line 123 is an open line from port 122 to the tank or sump 104. This construction permits and determines the rate of movement of piston 63 to traverse the diamond across the face of the Wheel being trued at the proper desired speed, While the diamond or trueing tool is immediately fed into the wheel the desired amount eliminating the possibility of a simultaneous infeed and traverse feed of the tool and a resultant tapered flange on the end of thed Wheel, as would be the case if the tool were fed toward the wheel slowly. However when retrueing the diamond or trueing tool to its initial normal position the valve 95 may be opened, as above described, to by-pass the feed rate valve 130 and rapidly return the parts to their initial positions.

Froml the foregoing description it Will be noted that there has been provided a single control member for selectively controlling a plurality of valves for effecting movement at varying rates of individual parts or units of a machine tool organization.

What is claimed is:

1. In a device of the class described the combination with a plurality of movable units, an hydraulic circuit for actuating each unit comprising a valve therein, a pressure source, a

valve block slidably supporting the valves, a valve shifter adjacent the valves for selective engagement therewith, means determining the operative connection of the valve shifter with the valve, said means comprising a plate operatively associated With theshifter and defining the movement thereof, thereby preventing movement of the valves simultaneously, means determining the rate of flow in each hydraulic circuit, means by-passing the rate determining means to permit a rapid now of the circuits, and means operable by the valve shifter for actuating the rapid traverse means, said means comprising a pivotally mounted actuator, a pusher, and a cam face carried by each valve for engagement with the pusher when moved by the valve actuator.

2. In a mechanism of the class described the combination of a bed, a pair of opposed grinding and regulating wheels forming a grinding throat therebetween and having an entrant end designating the operators position, a guard for each of the wheels and each forming a support for a truing mechanism for operation on its enclosed Wheel, a slide on each support for movement transversely of its wheel, a truing toolon each slide for movement toward the operative face of its Wheel, an hydraulic motor associated with each slide for effecting its transverse movement, an hydraulic motor associated with each truing tool for effecting its infeed movement, a single source of hydraulic pressure including an hydraulic medium for operating all of said hydraulic motors, a pair of valves each controlling the traverse and feed motor of the truing tool of one of the wheels, a universally adjustable manually actuable lever within convenient reach of the operators station for selecting and actuating the desired valve for operating the motors of either wheel truing mechanism, means for defining the path of movement of the lever for insuring proper operative connection between the lever and the desired valve, rate control means for determining the rate of flow of the medium, and means operable by said lever for by-passing the rate control valve.

3. In a mechanism of the class described the combination of a bed, a pair of opposed grinding and regulating Wheels mounted thereon and forming a grinding throat therebetween having an entrant portion forming the operators station, a guard supported by the bed and enclosing each wheel, said guards each having formed thereon a supporting guideway, a slide mounted on each guideway, a truing tool mounted on each slide, an hydraulic motor operatively connected with each slide for effecting its transverse movement relative to its wheel, an hydraulic motor for actuating each truing tool toward its wheel, a single source of hydraulic pressure including an hydraulic medium for operating said motors, a pair of valves one for the motors of the truing mechanism of each wheel for connecting the hydraulic medium therewith, a housing enclosing the valves and secured to the bed, a manually actuable lever carried by the housing within convenient reach of the operators station for selectively operating either of the valves and thereby selectively truing the operative face of either of the grinding or regulating wheels without leaving his normal station, 'a common means for controlling the rate of flow of the hydraulic medium to thereby control the rate of operation of the several motors, by-pass means operable to render the rate control means inoperative to thereby rapidly actuate the motors, and connections between the by-pass means and the manually actuable lever for operation of said by-pass means by the lever.

4. In a mechanism of the class described the combination of a bed,- a pair of opposed grinding and regulating wheels mounted thereon and forming a grinding throat therebetween having an entrant portion forming the operator's station, a guard supported by the bed and enclosing each wheel, said guards each having formed thereon a supporting guideway, a slide mounted on each guideway, a truing tool mounted on each slide, an hydraulic motor operatively connected with each slide for effecting its transverse movement relative to its Wheel, an hydraulic motor for actuating each truing tool toward its wheel, a single source of hydraulic pressure including an hydraulic medium for operating said motors, a pair of valves one for the motors of the truing mechanism of each wheel for connecting the hydraulic medium therewith, a housing enclosing the valves and secured to the bed, a manually actuable lever carried by the housing within convenient reach of the operators station for selectively operating either of the valves and thereby selectively truing the operative face of either of the grinding or regulating wheels without leaving his normal station, a common means for controlling the rate of flow of the hydraulic medium to therebyvcontrol the rate of operation of the several motors, by-pass means operable to render the rate control means inoperative to thereby rapidly actuate the motors, and connections between the by-pass means and the manually actuable lever for operation of said by-pass means by the lever, said by-pass means including a valve, a pivotally mounted actuator, and a sliding plunger engaging said valve and operable by the lever to open said valve.

5. In a machine tool organization the combination of a bed, a pair of slides mounted thereon for movement relative thereto, hydraulic means individual to each of said slides for effecting its movement, an hydraulic medium for said hydraulic means, a separate valve for controlling the flow of the hydraulic medium and the operation of the hydraulic means for each slide, a stem extending from each valve, a shifter spool on each stem and each spool being provided with a circumferential groove, a shifter adapted to be selectively engaged with the circumferential groove of each spool for eifecting the movement of its valve, and yielding means positioning said spools relative to the valve stems whereby the shifter spools may be actuated beyond the limit of shifting of the valve.

6. In a machine tool organization the combination of a bed, a pair of slides mounted thereon for movement relative thereto, hydraulic means individual to each of said slides for effecting its movement, an hydraulic medium for said hydraulic means, a separate valve for controlling the ow of the hydraulic medium and the operation of the hydraulic means for each slide, a stem extending from each valve, a shifter spool on each stem and each spool being provided with a circumferential groove, a shifter adapted to be selectively engaged with the circumferential groove of each spool for effecting the movement of its valve, yielding means positioning said spools relative to the valve stems whereby the shifter spools may be actuated beyond the limit of shifting of the valve, adjustable rate control means to control the rate of fiuid through the valve and consequently the rate of movement of the slides, and means associated with the valve shifter spools for rendering the rate adjustment means inoperative.

7. In a machine tool organization the combination of a bed, a pair of slides mounted thereon for movement relative thereto, hydraulic means individual to each of said slides for efwhereby the shifter spools may be actuated beyond the limit of shifting of the valve, adjustable rate control means to control the rate of fluid' through the valve and consequently the rate of movement of the slides, and means associated with the valve shifter spools forv rendering the rate adjustment means inoperative, said means including a plurality of cam faces associated with each valve spool, and means engageable with and operable by the said cam faces.

FREDERICK S. HAAS.

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